Hydraulic speed control for lathes



March 3, 1931. w. H. FOSTER HYDRAULIC SPEED CONTROL FOR LATHE-S FiledMarch 18, 1929 6 Sheets-Sheet 1 M H m M March 3, 1931. w. H. FOSTER HHYDRAULIC SPEED CONTROL FOR LATHES s Shets-Sheet 2 Filed March 18, 1929WI mm mm MR N h% R mm mm m w i mm HA wm a f U 4 m l 5 i \1 7 0 a, a, a oe I- W O O 0 n Q 8 O O Q ll 3 q {:14 m R bu R fin N m m I 1 u x i u A v9 Nb 3 RN bNN QR NN- O O mum. O O O @Q \i- Q N N U a 0 w 9 m llxllbl [Ii I a; A) a 0 Nb m hm mm Rum mum NMW @NQh g kh wh N m NW kwwmqw E 1mLflm' NY .nhh m 6 Sheeis-Sheet 3 [war/1 0? Wdam EJ 05151,"

b QDN a Q m N mow Rm 'WJQQ wm e mm 9 M March 3, 1931. w. H. FOSTER IHYDRAULIC SPEED CONTROL FOR BATHES Filed March 18. 1929 March 1931. w.H. osTarz HYDRAULIC SPEED CONTROL FOR LATHES Filed March 18, 1929 6Sheets-Sheet 4 OWN March 3, 1931. w. H. FOSTER HYDRAULIC SPEED CONTROLFOR LATHES 6 Shee ts-Sheet 5 Filed March 18, 1929 March 3, 1931. w. H.FOSTER HYDRAULIC SPEED CONTROL FOR LATHES Filed March 18, 1929 6Sheets-Sheet 6 5 A I I & i:

I Patented Mar. 3, 1931 UNITED STATES PATENT OFFICE WILLIAM H. FOSTEIII,F ELKHART, INDIANA, ASSIGNOR TO FOSTER MACHINE COM- PAN'Y, OF ELKHART,INDIANA, A CORPORATION OF INDIANA HYDRAULIC SPEED CONTROL FOR LATHESApplication filed March 18, 1929. Serial No. 347,814.

This invention relates to hydraulic or fluid-pressure means forcontrolling .the

speed of rotation of a lathe spindle and while particularly adapted 'to'use in connection with lathes, it may also be found to be useful inother machines having a rotatably driven part, the speed of rotation ofwhich is desirably varied from time to time. p

The principle object of the invention is to provide means forcontrolling the speed of rotation of a part such as a lathe spindle,which controlling means is especially simple in character andmay bemanipulated by the operator of the machine with the greatest of facilityso that his attention to the work need not be materially distracted.

Other objects of the invention are to provide hydraulic orfluid-pressure actuated means for controlling the speed of the spindle;to provide such fluid-pressure control means which may be controlledthrough the agency of a single valve which of itself may be quickly andeasily adjusted to effect the desired spindle speed adjustment; toprovide mechanism whereby the spindle may be selectively driven at anyone of a plurality of speeds in either forward or reverse direction; toprovide conveniently controlled means for effecting forward or reverserotation of the spindle and also for stopping the spindle; to providespeed control mechanism which is adaptable to any desired number ofspeed changes and in general, it is the object of the invention toprovide improved control means for controlling the operation of thespindle of a lathe.

Further objects and advantages of my invention will be understood byreference to the following specification and accompanying six sheets ofdrawings wherein I have illustrated a part of a lathe including thespindle and mechanism for drivin the spindle selectively at any one of aplurality of speeds in either forward or reverse direction.

In the drawings:

Fig. 1 is an end view of the front end of'a lathe head, that is, lookingat the work end of the lathe spindle.

Figs. 2. 3, and 4 are sections on the lines 2-2, 3-3, and 4-4,respectively, of Fig. 1.

' Fig. 5 is a section on the line 55 of Fi 4; Fig. 6 is a plan, certainparts bein bro en away, of a part of the mechanisms own in Fig. 1, thegeneral location of such parts being indicated by the line 6--6 in Fig.1.

Fig. 7 is a section on the line 77 of Fig. 6. Fig. 8 is a section on theline 8 -8 of Fig. 1. Fig; 9 is a development of a valve core whichappears in Figs. 4 and 5..

Figs. 10, 11 and 12, illustrate modifications of the structure shown inFigs. 1 to 9, inclusive, whereby the speed range of the spindle isincreased, or decreased Fig. 10 being an end viewsimilar to Fig. 1,and'Fi s. 11 and 12 being sections on the lines 111 1 and 12-12respectively, of Fig. 10.

Referring now to the drawings, I have shown a part of a lathe whichincludes a lathe bed 15 on which is mounted at one end, the spindle head16 which includes a spindle 17. which, in the present instance, consistsof a hollow or tubular shaft-like member through which stock may beadvanced into position wherein the usual cutting or other tools mayperform their usual functions on the said stock.

The head 16 includes mechanism, which I will presently describe, mountedin a casing which in this instance consists of an upper part- 18 and alower part 19', the two being secured together by means of bolts, or inany other suitable manner well-known in the art and hence not shown inthe drawings. The upper casing part 18 may be provided with a coverplate 20 which may be made integral therewith but preferably is made aseparate part and removably secured to the said upper casing part 18.The head casing as a whole is of such construction it will hold aquantity of lubricating oil which serves to lubricate the mechanism, andsupply oil for operating a pump which in turn operates the clutches, thearrangement being such that some 'of the parts of the said mechanismarepartly immersed in the oil which is normally in the bottom of thecasing, the said immersed parts The spindle 17 is rotatably mounted inthe motor or around a pulley carried by a line power shaft. A smallerpulley may be provided on the main drive shaft 23 for facilitating beltdriving of another part of the lathe mechanism or some other mechanism,or the said smaller pulley 25, may be used for driving the main driveshaft 23 at a different rate of speed than is conveniently obtainable byuse of the large pulley 24.

A plurality of driving connections between the main drive shaft '23 andspindle 17 are provided and include counter'shafts 26 and 27 whichsupport certain mechanism I am about to describe.

The main drive shaft 23 is provided with gears 28 and 29 which are keyedthereto so as to rotate therewith, the said gears being of differentpitch diameters. On the counter used.

shaft 26, I provide gears 30 and 31 which are formed integral withor'mounted on clutch parts 32 and 33 respectively, and mesh with themain drive shaft gears 28 and 29 respectively. The clutch parts 32 and33 are each rotatably mountedon the shaft 26, suitable bearingbushings'being provided if desired, and an intermediate clutch part 34 which issphned or otherwise non-rotatably mounted on the shaft 26 is providedfor selectively clutching the clutch parts 32 and 33 to the countershaft 26. It will be understood that although the clutch 34 isnon-rotatablv mounted on the counter shaft 26, it may be moved axiallythereof so as to effect the said clutching operation, suitable frictiondiscs, indicated at 35, being provided in accordance with well knownpractice in the clutching art, for effecting the desired non-slippingfrictional engagement between the shaft clutch part 34 and loose clutchparts 32 and133. Tooth clutches or other devices may also be Accordingto my present invention, '1.

provide hydraulic or fluid-pressure actuated means for controlling thefast clutch part i 34 so as to-clutch either of the loose clutch 7 parts32 and 33 to the counter shaft 26. In

the present instance, this fluid-pressure control mechanism includes acylinder'36fin which a piston 37 carried by a piston rod The pisshaft 26being drilled out as 'indicated'at 39 in any suitable manner suchfor'this' purpose. Adjacent its inner end, the piston rod 38 is providedwith a cross pin 40 which extends diametrically through. the shaft 26,anielongated slot 41 being provided in theshaft' for permitting the pin40 to move axially of the shaft in order that the clutch part 34 may bemoved from one lfosition to another to clutch the clutch parts 32 and 33to the counter shaft 26.

Axial movement of the clutch parts 32 and 33 alongthe shaft. 26 whensubjected to the pressure of the clutch part 34, is prevented by meansof collars 42 and 43 which are threadedly mounted on the shaft adjacent,the outer ends of the hubs of the said clutch parts 32 and 33. Thecollars 42 and 43 are preferably split and clamped in place by means ofclamping bolts, as indicated at 44 and 45, in a well-known manner.

It. Will be apparent to those skilled'in thev art that the abovedescribed mechanism is such that the counter shaft 26 may be rotatedselectively at either one of two speeds becauseof the difference in theratios of the pitch diameters between the meshing gears .28 and 30, and29 and 31. The clutch mechanism 32, 33 and 34 and its associatedgearing, therefore, constitutes a driving unit which is selectivelyengageable to drive the counter shaft 26 at either one of two speeds.For convenience in further reference, this unit maybe designated A.-

A second driving unit indicated generally at B, similar to the abovedescribed unit is associated with the counter shaft 26, being located atthe left hand end of the said shaft as shown in Fig. 2. This second unitincludes clutch parts 46 and 47 which are rotatably mounted on theshaft26 and an intermediate clutch part 48 which is non-rotatably but axiallymounted on the counter shaft so that it may be moved into position foroperatively connecting either of the clutch parts 46 and 47 to thecounter shaft 26. The clutch parts 46 and 4.7 are held against axialmovement under the influence of the pressure of theclutch part 48, by

is controlled through the agency of a cross pin 54 carried by a pistonrod 55 and a piston 56 secured to said piston rod and adapted to bemoved axially in a cylinder 57 by means of hydraulic or fluid-pressure.

noted that clutch parts46 and 47 and the It will be a J respective gearscarriedthereby may each be rotated at the shaft 26.

The second counter shaft 27 is rotatably two speeds of the countermounted, as shown in Fig. 2.

A third driving unit C similar to" the first and second unit-s abovedescribed, is mounted on the counter shaft 27 and is operativelyconnected with the second unit on the counter shaft 26 above described.This third unit includes clutch members and 61 which carry gears 62 and63 respectively, the said gears being formed integral with therespective clutch members or secured thereto so as to rotate therewith.The clutch parts 60 and 61; are rotatably mounted on the counter shaft27 and an intermediate clutch part 64 is nonrotatablybut axially slidablmounted on the counter shaft 27 so as to operative to effectclutchingengagement between either of the clutch parts 60 'or 61 and thecounter shaft27. The clutch part 64 may be controlled through the agencyof a cross pin 65 carried by a piston rod 66 ha 'ng a piston 67 disposedin a cylinder 68 arid a dapted to be axially moved in the cylind rhydraulic or fluid-pressure. I

Driving units B and C are connected by by means of? I gearing so thatthe unit B is operative to effect rotation of the clutch parts of unitC. The means for so connecting units B and C consists of gear members 69and 70 which are rotatably mountedon the lathe spindle 17 through theagency of ball bearings 71 and 72.- In the present instance, the gear69,is

rovided with elongated sleeve or hub part 73 on' which the gear 70 ismounted by means of a hub 74, the gear 70 being keyed to the gear 69 bymeans of a key 75 so that gears 69 and 70 are rotatable asa unit aboutthe spindle 17 The gear 69 meshes with the gear 52 of drivin unit B andgear 70 meshes with gear 53 of t c said driving unit B. It will now beseen that the gear unit, 69, 70, 73, may be rotated at any one of fourspeeds since it is operatively connected to each of the gears 52 and 53of the driving unit B which gears are each rotatable at two differentspeeds.

The gear 70, in addition to meshing with the gear 53.0f driving unitB,.meshes with gear 63 of driving unit G. Hence, the gear 63 and clutchpart 61 are rotatable selectively at anyone of the four speeds at whichvthe gear unit'69, 70, 73 is rotatable. The clutch part 60 and gear 62are operatively connected to the gear unit 69, 70, 73 through the agencyof a gear 76 which is mounted on the hub 73 and-keyed thereto by the key75. Hence, the hub 60 and gear 62 are also rotatable selectively at anyone of four different speeds." It will be apparent from an inspection ofthe drawings that the various gear ratios are such that the clutch parts60 and 61- 'of driving unit C are each rotatable at four differentspeeds and that the four speeds of each of the said clutch parts aredifferent from the four speeds of the other clutch part. Hence, thecounter shaft 27 may be rotated selectively at any one of eight-speeds.

mounted on the Said counter shaft v27. In the.

present instance, the clutch part 77 is rovided with a sprocket 80formed integra on the hub of the clutch part 77 and the clutch part 78is provided with a gear 81 which, in the present instance, is formedindependently of the said clutch art and non-rotatably mounted on thehub of the said clutch part, a key 82 being provided to lock the partsagainst relative rotation. A gear 83 is nonrotatably mounted on thespindle 17 by means of a ky 84"and meshes with the gear 81 carried bythe clutch part 78." It will be apparent that by clutching the'clutchpart 78 to the shaft 27, the spindle 17 may be rotated in one, say theforward direction, at any one of eight speeds. A sprocket 85 is alsomounted The counter shaft 27 and lathe spindle 17.

on the spindle 17 and held against rotation I thereon by means of-thesaid key 84 and a chain 86 connects the sprocket 85 with the sprocket 80so that when the clutch part 77 of the driving unit D is clutched to thecounter shaft 27, the spindle may be rotated in tlzle' reverse directionat any one of eight s cc s. I

The clutch part 79 of the unit D may be controlled by fluid or hydraulicpressure in a manner similar to that in which-the corresponding clutchelements of driving units A, B and C are controlled. Accordingly, I

provide a cylinder 87 in'which a piston 88 is units A, B and C bycontrolling the admission and discharge of fluid-pressure in the saidcylinders 36, 57 and 68. The said valve is indicated generally at 91 inFigs. 1 and 4 and includes a core 92 which is rotatably mounted in acasing 93, the latter being mounted in the upper housing part 18 in anyand 95 and a plurallty of discharge apertures 96. The core part 92 isbored out as shown at 97 and the end wall 98 of the valve housing istapped as shown at 99 to receive a pipeline connection 100 whichconnects with an oil pump 101 of any suitable type which is mounted onthe inside of the head casing or housing so as to be capable ofsupplying oil under pressure from the supply of lubricant contained in.the said head 16. The pump 101 may be of a gear type, well-known in theart, and may be driven by any suitable gear or chain driving connectionwith the counter shaft 26 or any other rotating part of the mechanism.Such connection, being well within the skill of a mechanic versed inthis art, is omitted in the drawings to facilitate clcarn'ess ofillustration.

The apertures or ports 94 and 95 in the valve housing 93 are tapped toreceive pipe line fittings 94' and 95' respectively, and the said portsare arranged to alternately. extend upwardly and downwardly as clearlyshown in Figs. 4, and 6, so as to facilitate positioning of the variouspipe lines and also so as to provide room to permit the respectivefittings to be screwed into place without being obstructed by theadjacent fittings. Thus, compactness of the valve structure is also madepossible. Each of the ports 94 and 95 in the valve housing 93 constituteboth inlet and outlet ports for the respective ends of the cylinders towhich they are connected.

In Fig. 4, the ports 94 and 95, six in number, are also designated a, b,0, d, e and f f r greater convenience in referring thereto and v forfacilitating description of the connections from the cylinders 36, 57and 68 with the said valve port-s. In Fig. 2, I have indicated theopposite ends of the c linders by the reference letters a, b, a, d, e anf according to the similarly designated valve ports to which therespective ends of the cylinders are connected. In other words, the porta in the valve is connected by a suitable pipe line to the outer end aof the cylinder68, the port 6 to the inner end of the cylinder 68 etc.etc.

By an inspection of Figs. 2 and 4, it will be seen that the valve 'inthe position shown causes fluid pressure to be supplied to the outerportion of the cylinder 68, and the inner portions of the cylinders 36and 57 so that the respective clutch parts assume the posltions shown inFig. 2. For establishing commumcation between the drilled out chamber 97in the valve core and the ports a to f mclusive, the said core isrovided with passageways 102-102 extending from the chamber 97 to theoutside of the core and adapted to com- I municate with the ports 94 and95. The core is also provided with a plurality of annular grooves 103which extend therearound but which do not communicate with the chamber 197. A plurality of recesses 104 in the outer surface of the corecommunicate with and extend laterall from the said grooves 103 so as tobe capab e of efiecting communicatlon between the ports 94 and 95 andthe said grooves. The discharge 0 enings '96 in the valve housing 93 arealigne with the grooves 103 so that any existing pressure in the ends ofthe cylinders with which the grooves communicate (through the recesses104 and valve ports), is relieved through the said discharge openings96. It will be seen by an inspection 0 Fig. 5 that the ports designated6, d, and e are in communication with the res ective discharge openings96 so that the fluid-pressure in the cylinder portions, 6, d and e isthereby relieved. 'It will now be apparent that the valve structureis-such that when pressure is supplied to one end of a cylinder, theexisting pressure in the other end is simultaneously relieved.

The valve core 92 is provided with an extensipn 105 to which anoperating handle 106 may be secured in any suitable manner, as indicatedin Figs. 1 and 6. The operating handle 106 is provided with a pointer107 which indicates, by pointing to suitable indicia, the position ofadjustment or speed for which the spindle operating mechanism is set.

In Fig. 9, I have shown a development of the valve core 92 and thefollowing tabulation will serve to indicate the eight positions ofadjustment for the core and the connections established in eachposition. In the following tabulation on is used to indicate thatfluid-pressure is supplied through the respective orts indicated and tothe corresponding cylinder end ports. Oil is used to indicate that thepressure is relieved.

Ports Core lel with'the core receivmg bore 109 an passageways 112, 113and 114 are provided whereby fluid under pressure supplied to thepassageway 111 may communicate with the annular grooves 115 and 116provided in the valve core. Fluid under pressure is supplied to thepassagewa 111 by means of a pipe connection 117 rom the pump 101. Thevalve body 108 is also provided with openings 118 and 119 which aretapped to receive pipe line connections 120 and 121 which arerespectively connected to the oppo= site end portions of the cylinder87. The valve core is centrally. cored out as indicated at 112 andprovided with apertures 123 and 124 for establishing communicationbetween the pipe lines 120 and 121 and the chamber 122. The valve core110 is also provided with recesses 125 and 126 which communicate' withthe openings 123 and 124 respectively and extend lengthwise of the valvecore from the respective openings.

As shown-in Fig. 8, the valve is in a neutral position of adjustment inwhich fluid pressure is.not supplied to either end portion of thecylinder 87. It will be understood that if the valve is adjusted so thatfluid under pressure may pass from the passageway 111 through theopening-112, around the annular groove 115 and through the 0 opening 118into the pipe line 120 and into the corresponding end of the cylinder87, the piston 88 will be caused to move accordingly and thereby effectoperative connection between the counter shaft 27 and one of the clutchparts of the unit D. When the valve is so adjusted, it will be seenthatthe pressure in the opposite end of the cylinder will be relievedthrough the pipe line 121, the recess 126, opening 124 and the cylindercham her 122 which is open at the inner end of the valve coreso that thefluid may flow from this chamber back into the supply of lubricantcontained in the lathe head casing. The valve may also be adjusted so asto effect communication between the passageway 111 and the pipe line 121so as to supply fluid-pressure to the other end of the cylinder 87 inwhich case the pressure is relieved from the opposite end of thecylinder through the pipe line 120, the recess 125, aperture 123 andchamber 122.

In addition to controlling the driving unit D, the valve 107 controlsbrake mechanism best shown in Figs. 1, 6 and 7. The brake mechanismcomprises a brake drum 127 preferably formed as an integral part of thegear 83, and a brake lever 128 pivotally mounted by means of a stud 129carried by the head casin The brake lever 128' may be provided with asuitable friction brake lining which bears on the brake drum 127 to stoprotation of the same. For forcing the brake lever 128 into brakingengagement with the brake drum 127, I provide a cylinder'130 in which aplunger. 131 is slidably mounted and adapted to be forced outwardly bymeans of fluid-pressure supplied'by the P 101 and controlled by the saidvalve 107. Thef'ylinder member 130 is attached to the end wall of'thehead casing 18 in any suitable manner and the cylinder chamber isconnected by means of a pipe line 132 to a assageway 133 in the u perart of the va ve body or housing 108' see ig. 7 As shown in Fig. 7, thepassageway 133 communicates with the annular groove 116 provided in thevalve core, which groove is in communication with the assageway 111through theaperture 114, ence, fluld under pressure will flow from thepassageway 111, through the annular groove 116 and passageway 133 intothe cylmder chamber 130 to force .the plunger 131 downwardly, thereby toeffect frictional engagement between the brake lever 128 and brake drum127. When the valve 107 is in position to effect a neutral position ofthe clutch member 79 of the drivlng unit D, (as shown in- Fig. 8) thebrake 128 is applied to hold the spmdle against rotation. When the valve1s adjusted to effect operative engagement between one of the clutchparts of the driving unit D- and the counter shaft 27, pressure in thebrake cylinder chamber 130 is relieved. For relieving the pressure inthe brake cylinder chamber, the valve core 110 is provided with openings134 and 135 which are adapted to register with the inner end of thepassa eway 133 so that the fluid in the cylinder chamber 130 may flowbackwards from the chamber through the passageway 133 and one of theopenings 134 and 135, into the chamber 122 and thence to the supply oflubricant.

It will be seen that the arrangement of the valve 107' is such that whenthe driving unit D is in neutral position, the brake is applied to holdthe spindle against rotation. It will also be seen that in changing thedirection of rotation of the spindle, the s indle is efiectively stoppedfrom rotating efore the reverse driving connection can be completed.Such automatic braking of the spindle is desirable in that .it avoidsover straining of the driving parts which might otherwise occur inchanging the direction of .rotation of the spindle 17. A hand lever 136pivoted as indicated at 137 and connected at its inner end as shown at138 to the outer end of the valve core 110 is provided for facilitatingmanual adjustment of the valve 107.

The above described mechanism whereby eight distinct speeds are obtainedfor the spindle, is susceptible of adaptation by the addition of furtherdriving units such as A,

B and C, to provide other ranges of speeds.

For instance, in Figs. 10 to 12 inclusi've, I

have shown an arrangement, generally similar to the arrangement showninFigs. 1 to 9 inclusive, but in which sixteen speeds are provided. Inthis modification a selectively engagable driving unit E is mounted onthe main drive shaft indicated by the reference character 139 andcontrolled through the unit E and the, gear 145 meshes with the gear 30on the counter shaft 26. Another gear 148 also carried by the extracounter shaft 142 meshes with the gear 31 onthe counter shaft 26.

By an inspection of Fig. 11 it will be. seen that each of the clutchparts 32 and 33 of" driving unit A are rotatable selectivelyiat eitherone or two speeds and that the clutch parts 46 and 47 of driving unit Bare each rotatable at any oneof four speeds. Hence, the range of speedsof parts of the driving units A and -B is double the range of speeds ofthe same units in the arrangement shown in Figs. 1 to 9 inclusive.Accordingly, the gear unit 69, 7 0 and 73 would be rotatable selectivelyat any one of eight speeds and the clutch parts 60 and 61 of drivingunit C would each be selectively'at any one of eight speeds so that thecounter shaft 27 may be rotated at any one of sixteen speeds. v

In Fig. 12 I have shown a sectional view of the valve forcontrollingfour driving units instead of .three. The construction of the valve asshown in Fig. 12 is similar to-that of the valve shown in Fig. 4 but" isextended to provide control for the additional driving unit E. Thoseskilled in this art will readily understand the manner in which thevalve is arranged, particularly in view of the complete'description ofthe valve provided for the eight speed arrangement, andhence it is notdeemed necessary to supply a detailed description or illustration of themodified or extended valve mechanism. f i Obviously, the range of speedsmay be greatly increased but, generally speaking, a range of eightspeeds is sufliclent for most practical purposes and it is comparativelyseldom that as many as sixteen speeds are reuired. In view of the factthat more than slxteen speeds are seldom required, and in view of thefact that a person skilled in the art, after the present disclosure, canreadily produce an arrangement according to my invention for affording agreater speed range, I do not deem it necessary to illustrate 'nordescribe an arrangement for affording such a furtherincreased speedrange. In the above specification I have referred to hydraulic pressureor fluid pressure in a broad sense and without intending to limit myselfto the use of any particular-fluid under pressure. As above brought out,I have found it convenient in the present instance to use a part of thelubricating oil which is contained parts without departing from thespirit of my invention, the scope of which should be determined byreference to the following claims, the same being construed as broadlyas possible consistent with the state of the art.

I 'claimas my invention: 3 1. In a lathe of the class described, the

combination of .a spindle, a rotatably mounted counter shaft, means forselectively effecting rotation of said counter shaft at either one oftwo speeds, a pair of clutch members rotatably mounted on said countershaft, a pair of gear members of different pitch diameters respectivelyconnected to said clutch members so as to be rotatable therewith, meansfor selectively clutching said clutch members and their associated gearmembers to said-counter shaft, each of said gear members being therebyrotatable selectively at either one of two speeds, a second countershaft, a pair of clutch members rotatably mounted on said second countershaft, a driving connection between each of said last mentioned clutchmembers and said gear members whereby. said last mentioned clutchmembers are each rotatable atfour speeds, means for selectivelyclutching said last mentioned clutch members to said sec- -ond countershaft whereby tnelatter is selectively rotatable at any one of eightspeeds, and a drivin connection between said second counter sha tandsaid spindle whereby the 'latter is adapted to be selectively drivenat said gear members being thereby rotatable 'selectlvely at either oneof two speeds, a sec .ond counter shaft, a pairof clutch members clutchmembers rotatably mounted onsaid combination of a spindle rotatablymounted on said second counter shaft, a driving connection between eachof said last mentioned clutch members and said gear members whereby saidlast mentioned clutch members are each rotatable at four speeds,fluid-pressure controlled means for selectively clutching said lastmentioned clutch members to said second counter shaft whereby the latteris selectively rotatable at any one of eight speeds, a drivingconnection between said second counter shaft and said spindle wherebythe latter is adapted to be selectively driven at any one of said eightspeeds.

3. In a lathe of the class described, the combination of a spindle, 'arotatably mounted counter shaft, fluid-pressure controlled means forselectively effecting rotationof said counter shaft at either one of twospeeds, a pair of clutch members rotat-' ably mounted on said countershaft, a pair of gear members of different pitch diameters respectivelyconnected to said clutch members so as to be rotatable therewith,fluidpressure controlled means .for selectively clutching said clutchmembers and their associated gear members to said counter shaft, each ofsaid gear members being thereby rotatable selectively at either one oftwo speeds, a second counter shaft, a pair of second counter shaft,fluid-pressure controlled means for selectively clutching said lastmentioned clutch members to said second counter shaft, gear members ofdifferent pitch diameters respectively associated with each of said lastmentioned clutch members, and a driving connection between each of thegear members on said first mentioned counter shaft and each of the gearmembers on said second counter shaft, said driving connection comprisinga rotatably mounted sleeve, gear driving connections between said gearmembers on said first mentioned countershaft and said sleeve, wherebysaid sleeve is selectively rotatable at any one of four speeds, gearconnections between said sleeve and each of the gear members on saidsecond counter shaft whereby each of said last men tioned gear membersis rotatable selectively at any one of four speeds and whereby saidsecond counter shaft is selectively rotatable at any one of eightspeeds, and a driving connection between said second counter shaft andspindle.

4. In a lathe of the class described, the a rotatably mounted countershaft, flui' -pressure controlled means for selectively effectingrotation of said counter shaft at either one of twospeeds, a pairof'clutch members rotatmembers so as to be rotatable therewith,

fluid-pressure controlled means for selectively clutching said clutchmembers and their associated gear members to said counter shaft, each ofsad gear members being on said second counter shaft, said drivingconnection comprising a rotatably mounted sleeve, gear drivingconnections between said gear members on sald first mentioned countershaft-and said sleeve, wherebysaid sleeve is selectively rotatable atany one of four speeds, gear" connections betweensaid sleeve and each ofthe gear members on said second counter shaft whereby each of said lastmentioned gear members is rotatable selectively at any one of fourspeeds and whereby said second counter shaft is selectively rotatable atany one of eight speeds, a single valve means for controlling all ofsaid fluid-pressure controlled means for adjusting said clutch membersto drive said second counter shaft at any one of said eight speeds, anda driving connection between said second counter shaft and said spindle.

5. In a lathe of the class described, the combination of a. spindle, arotatably mounted counter shaft, fluid-pressure controlled means forselectively effecting rotation of said counter shaft at either one oftwo speeds, a pair of clutch members rotatably mounted on said countershaft, a pair of gear members of different pitch diameters respectivelyconnected to said clutch members so as to be rotatable therewith,fluid-pressure controlled means for selectively clutching said clutchmembers and their associated gear members to sa1d counter shaft, each ofsaid gear members being thereby rotatable selecclutch members to saidsecond counter shaft,

gear members of diflerent pitch diameters respectively associated witheach of said last mentioned clutch members, and a driving connectionbetween each of the gear members on said first mentioned counter shaftand each of the gear members on said second counter shaft, saiddriving-connection comprising a rotatably mounted sleeve, gearconnections between said gear members on said first mentioned countershaft and said sleeve.

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whereby said sleeve is selectively rotatable at any one of four speeds,gear connections between said sleeve andeach of the gear members on saidsecond counter shaft whereby each of said last mentioned gear members isrotatable selectively at any one of four speeds and whereby said secondcounter shaft is selectively rotatable at any one of eight speeds, asingle valve means for controlling all of said fluid-pressure controlledmeans for adjusting said clutch members to drive said second countershaft at any one of said eight speeds, forward and reverse drivingconnections between said second counter sha fit and said spindle wherebythe latter is selectively operable forward or reverse at any of saideight s eeds and fluid-pressure controlled means or selectively engagingsaid forward and reverse driving connections.

Si ned at Elkhart, Indiana, this 14th day of arch, 1929.

. a WILLIAM H. FOSTER.

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